Hydraulically controlled automatic die sinking machine



June 4, 1935. B. sAssEN 2,003,557

HYDRAULICALLY CONTROLLED AUT OMATIC DIE SINKING MACHINE Filed Aug. 17, 1932 5 Sheets-Sheet 1 3 r 14.) C 14x01;

Bi/F/VAWD j4555/V WW SHOMWAJ June 4, 1935. B. SASSEN V 2,003,557

HYDRAULICALLY CONTROLLED AUTOMATIC DIE SINKING MACHINE Filed Aug. 17, 1932 5 Sheets-Sheet 2 BEE/VARD 5/1555 F WMW B. SASSEN Jun 4, 1935.

HYDRAULICALLY CONTROLLED AUTOMATIC DIE SINKING MACHINE Filed Aug. 17, 1932 5 Sheets-Sheet 3 BEE/mm? Sassz-w June 4, 1935. B. SASSEN 2,003,557

HYDRAULICALLY CONTROLLED AUTOMATIC DIE SINKING MACHINE Filed Aug. 17, 1952 5 Shee t'5Sheet 4 I24 136 59 my B. SASSEN June 4, 1935.

HYDRAULICALLY CONTROLLED AUTOMATIC DIE SINKING MACHINE Filed Aug. 17, 1952 5 Sheets-Sheet 5 Patented June 4, 1935 PATENT OFFICE HYDRAULICALLY CONTROLLED AUTO- MATIC DIE SINKING MACHINE Bernard Sassen, Cincinnati, Ohio, assignor to The Cincinnati Milling Machine Company, Cincinnati, Ohio, a corporation of Ohio I Application August 1'7,

35 Claims.

' This invention relates to improvements in machine tools and more especially to machines for the performance of profiling, contouring and diesinking or similar operations.

One of theprincipal objects of the present invention is the provision of improved actuating mechanism for the moving parts of the machine which will facilitate relative movement of the work and cutter in both straight and curvilinear paths for the formation of desired continuous contoured surfaces on the work.

A further object of the invention is the provision of improved automatic controls for the respective movements of the work and tool which will facilitate thev accurate reproduction of a work piece in correspondence with a selected pattern and with a surface comparable both in shape and finish with that of the pattern being utilized A further object of the invention is the provision in connection with an hydraulically actuated machine of the character described including means for eilecting relative hydraulic movement of the tool and work piece in a plurality of angularly related directions, of means for automatically maintaining the selected feed rate in given directions constant irrespective of the relative resistances to movement of the parts in said respective directions.

' Another object of the invention is the provision in a machine of the character described of improved actuating mechanism for effecting a continuous uniform power flow to the parts to be shifted and including automatic control mechanism for varying the proportional distribution of said power to the individual units actuable thereby.

An additional object of this invention is to provide an improved hydraulic tracer control.

mechanism for machines of the character described in which the response of the parts controlled thereby is positive throughout the entire range of feed rates, thereby insuring maximum accuracy of reproduction of the patternwhen high feed rates are utilized with attendant momentum of the parts controlled.

Another object of the present invention is the provision of an improved hydraulic actuating and control mechanism for machines of the character specified in which the variation in proportional distribution of actuating medium to the respective shiftable units for effecting a change in the resultant path of relative movement between cutter and work shall be directly proportional' to the corresponding displacement of the pattern following tracermember.

1932, Serial No. 629,197

Other objects and advantages of the present invention should-be readily apparent by reference to the following specification considered in conjunction with theaccompanying drawings forming a part thereof and it is to be understood 5 that any modifications may be made in the exact structural details there shown and described within the scope of the appended claims without departing from or exceeding the spirit of the invention.

In the drawings:

Figure 1 is an elevational view of a machine embodying the improvementsof this invention.

Figure 2 is a fragmentary elevational view of a portion of the machine shown in Figure 1 and 15 as seen particularly from line 2-2 on Figure 1.

Figure 3 is a diagrammatic sectional 'view through the tracer and valve controlled thereby.

Figure 4 is a diagrammatic elevational view of the feeding mechanism for efiecting the rela- 2o tive advancement of the parts at each complete stroke thereof.

Figure 5 is a diagrammatic view illustrating the complete hydraulic circuit embodied in the invention and showing the distributor valve in one position of adjustment.

Figure 6 is a diagrammatic view of a modified form of hydraulic circuit for completely controlling the'movements of the parts and showing the distributor valve in the same position of adjustment as shown in Figure 5.

Figure 7 is a sectional view through the distributor valve and valve sleeve showing the distributor valve at one extreme position of adjustment.

Figure 8 is a sectional view through the distributor valve similar to Figure 7, but showing the valve in a position in between the positionsshown in Figures 5 and 7.

Figure 9 is a sectionalview similar to Figures 7 and 8 but showing the valve in a position between the position shown in Figure 5 and the extreme position'shown in Figure 10.

Figure l0 is a sectional view similar to'Figures '7, 8 and 9 but illustrating the valve at its other extreme position of adjustment opposite from. that shown in Figure 7.

Figure 11 is an enlarged transverse sectional view through the distributor valve and its sleeve as seen from line Hll on Figure 5.

Figure 12 is an enlarged transverse sectional view through the distributor valve and its sleeve as seen from line l2--I2 on Figure 5.

Figure 13 is an enlarged fragmentary elevational view of one of the slotted portions of the distributor valve forming a detail of the invention.

Figure 14 is a diagrammatic illustration of a pattern to be followed by the tracer during a traversing movement of the work and cutter.

Figure 15 is a diagrammatic illustration of a balance valve as used in this invention.

Figure 16 is a diagrammatic illustration of means for operating the valve shown in Figure 15 and {as seen particularly from line lie-l6 on'Figure Figure 1'7 is an hydraulic diagram of the manual means for effecting and controlling the operation of the machine.

In any machine intended for use in production of irregular profiled or contoured surfaces of such nature that they cannot be produced solely by individual straight line movements as is customary in ordinary milling machine practice, it is necessary that the work and tool operating thereon be supported for movement in two angularly related directions in a given plane such that the parts may be traversed one with respect to the other to cause the tool to move or be moved over the surface of thework and at the same time there must be a relative in and out movement or approach and retraction of the parts. By combinations of these two movements any straight or curvilinear surface may be formed on the work piece by the tool. These requirements are necessary in either what is known as profiling, when an outline or surface on the work-is to be formed not in excess of the path of the operative surface of the tool, and is equally necessary in the case of contouring, when the surface to be produced is greater than that engageable by a single path of movement of the tool. In the latter event, however, it is necessary that a third relative movement be provided for displacing the path of movement by successive increments or the like such that the entire surface of the work which it is desired tomachine will eventually be presented in operative relation to the tool.

In automatic machines such as those forming the subject matter of the present invention it is desirable that the control of these movements be entirely automatic as distinguished from individual manual adjustments for effecting the different movements of the parts. To accomplish this result, it has been customary in the prior art to make use of a pattern or guide corresponding to the shape to be produced on the work and some type of tracer or follower mechanism for engagemerit with the pattern or guide to determine the relative movement of the parts.

The present invention relates more particularly to an improved type of tracer mechanism which will satisfactorily follow patterns, whether of metal, wood or plastic materials, requiring relatively slight pressure contact between pattern and tracer, together with means for effecting appreciable amplification of the operative effect of the tracer movement rendering'the control thereby of extreme sensitivity.

It is to be understood that in utilization of mechanism of this character the tracer and pattern must be maintained in engagement one with! the other and the work and cutter must be correspondingly engaged and that the relative movement of work and cutter on the one hand and of pattern and tracer on the other, must be similar, although it will be-understood that the actual amount of movement may be either the same or different as long as the proportions of movement mined size in accordance with the relative proportions of movement.

The present invention contemplates the use of an hydraulic tracer device in which movement of the tracer point will be hydraulically converted with suitable amplification into mechanical movement for determining the coupling of the actuators with the several movable parts, which parts may comprise as independent jointly =shiftable units either the cutter and tracer as one unit and the work and pattern as a second unit, or the pattern and cutter as a unit and the work and tracer as the other unit.

In the preferred form of the invention here illustrated not only the tracer, but also the several shifting mechanisms are hydraulically operated, use preferably being made of a predetermined volumetric hydraulic flow for effecting the relative movements of the units just mentionedvone with respect to the other, it being understood that a portion of the movements in question may be transmitted to one unit and a portion to the other, or that one unit may be held stationary while a plurality of movements in different directions are transmitted to the opposed unit so long as the necessary relative approach and retraction and traversing movements are effected. In the present invention the determination of the rectilinear or curvilinear path of relative movement of the parts is eifected by a varian ce in the proportional distribution of the constant hydraulic flow to the several individual actuators and the proportional distribution controlling member is hydraulically coupled with the movable tracer point in such manner that the variation in distribution will be in the nature of a constant or progressively changing action and directly proportional to the deflection of the tracer in following the contour of the pattern in place of a pulsating or intermittent action as has been characteristic of the known structures hitherto suggested.

It will therefore be understood that the embodiment of the invention shown in the accompanying drawings is utilized for purposes of iilustration only of the general principles of the present invention, as. their possible alternative applications will be evident from the foregoing description of the underlying principles of the present invention.

In these drawings the work and pattern, have been shown as coupled together as one unit and the tracer and cuttingtool as a second unit. The first unit is given a longitudinal or what may be termed traversing movement, and the second unit a movement of approach and retraction relative to the first during said traversing movement, both under control of the interengaged pattern and tracer, while additional means are provided for effecting a shifting of the second unit to causethe tracer and cutter to traverse diiferent paths of the work and pattern in successive cutting operations in order that the desired contoured surface area may be produced on the work.

The machine as shown comprises a bed I0 having secured to one face thereof a support H having a work and pattern supporting table I2 mounted thereon. In order to guide the table l2 in its traversing movement it is provided with a dove-tail l3 received in a correspondingly shaped guideway formed in "the support ll. Rising above the bed I0 is a column l5 having formed on its one surface guides I6 and I! for a slide 18 movable relative thereto. The slide l8 has formed on its forward face a guide 9 received in .a suitable guideway formed on the adjacent face of a carriage 2|! for movement transversely of the slide. The carriage 20 carries the tracer mechanism as well as the cutter. The cutter 2| is secured to the forward end of a spindle 22 journaled in a bearing 23 formed integral with or securedto the carriage 20. A variable speed motor or prime mover 24'is secured to the carriage 20 having its shaft 25 connected with the spindle 22 as by means of a pinion 26 and a gear 21, the former being secured to the motor shaft 26 while the latter is secured to a projecting por-- tion of the spindle 22.

The table I2 and the parts supported thereby .are arranged to be traversed by the motor generally designated by the reference numeral 28. This may consist of a piston 29 secured to the table'by means of the piston rod 28'. The piston 29 is adapted to be actuated in opposite directions in its enclosing cylinder 30 carried by the support II, for which reason it has secured re-' spectively to its right and left hand ends, as.seen in Figures and 6, the conduits 3| and 32. The, other ends of these conduits 3| and 32 terminate at a reversing valve casing 33 containing a spool type reversing valve 34. The valve 34, as seen in Figures 5 and 6, has secured to it one end of a link 35, its other'end being pivoted at 36 to a lever 31. The lever 31 is pivoted intermediate its ends at 38 to a fixed part of the bed and through the lever 31 the valve may be manually shifted.

The carriage 20 is actuated toward and from the pattern and work by means of a motor 39, which may conveniently comprise a piston 39' having projecting from it a piston rod 40 connected, for example, at Mo to the rear end of the carriage 29. The piston 39 is enclosed within a cylinder 4| carried by a bracket or the like 42 attached to the rear end of the slide I8. The piston 39" is adapted to be reversely actuated through the cylinder 4| for which purpose it has, see Figures 5 and 6, respectively secured to its upper and lower ends conduits 43 and 44. Extending from 'the upper surface of each cylinder and from opposite ends thereof are suitable air bleeders which remove or drain all of the air'from the system to insure continuous smooth operation of the machine. These air bleeders are shown diagrammatically in Figures 5 and 6, those associated with cylinder 4| are in- I dicated by the numeral 4|, while those associated with the cylinder 30 are indicated by the numeral 30'.

In order to effect the vertical adjustment of the slide 8 it is provided on its rear surface with a nut 45 in threaded engagement with an adjusting screw 46 journaled at its upper end in a bearing 41 carried by the column IS. The lower'end of the screw is journaledin a bearing or bracket 48 attached to the column l5 beyond which the screw projects to receive a bevel gear 49. The gear 49 is meshed 'witha similargear 59 on one end of a transverse shaft 5| journaled in the bracket 48 and support For manually rotating the shaft 5| and thereby manually adjusting the position of the slide as for set-up purposes and the like, the end of the shaft 5| has secured to it a lever-52. D'uring'operationand to automatically incrementally adjust the slide 8, the shaft 5| carries inter-' mediate its ends a ratchet 53 adapted to be actuated successively by pawls 54 and 55, see Figure 4. The pawls 54 and 55 are pivotally mounted respectively to toggle arms 56 and 51 which are connected by a common pivot 58 to one end of a bell crank 59. The bellcrank 59 is pivoted at 6! to a stationary part of the. machine and has connected to its other arm as at 6| a slide rod 62.

The rod 62 is slidable through bearings 63 and 64 provided by the column l5 and is also slidablethrough an ear or lug 65 projecting from the adjacent side of the work table l2. Adjustably secured to the rod 62 are dogs 66 and 61 adapted to be engaged by the lug or car 65 during the travel of the .table |2 for axially shifting the rod 62- and oscillating the bell crank 59. The reverse movement of the table is accomplished automatically through a load and fire mechanism which has associated therewith the usual lost motion mechanism thereby providing a definite amount of table movement prior to each reversal. It is during this interval of movement that the dogs 66 or 61 are engaged for effecting the incremental feed, therefore, by varying the positions of the dogs 66 and 61 the amount of incremental feed for each table reversal may be varied. I

With the table travelling to the right, as seen in Figure 4,' the lug or ear 65 would engage the dog '61 and shift the rod 62 to the right, thereby oscillating the bell crank 59 in a clockwise direction causing the toggle arms 56 and 51 to straighten out, which through the arm 56 and its pawl 54-would rotate the ratchet 53 in a clockwise direction, the pawl 55 idly riding over the teeth of the ratchet. Reverse movement of the table I 2 or to the left would effect engagement between the lug 65 and dog 66 thereby oscillating the bell crank in a counterclockwise direction tending to spread the togglearms 56 and 51 outwardly.

This would cause the pawl 55 .which was elevated by the previous movement of the bell crank to engage behind the tooth on the ratchet to .rotate the ratchet again ina clockwise direction while the pawl 54 now is idly returned. From this it will be seen that reciprocation of the slide rod 62 in either direction effects rotation of the ratchet 53 in a constant clockwise direction, which through the shaft 5|, bevel gears 49 and 50, and screw 46 shifts the slide IS in a given direction, thereby causing the tracer and tool to engage with successive vertically displaced paths or zones of pattern and work.

The tracer mechanism illustrated in detail in Figure 3 comprises a tracer arm 68 having a ball .end 69 that contacts with the pattern 19.' The tracer arm 68 is provided on its inner end with an enlarged head 1| to which is secured a ring 221 to thereby form a recess 228 having a sharp corner 229 at the end thereof where the head 1| and ring 221 are joined together. Contacting with the sharp corner 229 is a knife edge formed on the end of a flange 236 integral with or secured 'to a sleeve or cap 12. The inner surface of the head 1| engages a knife edge contact band 13 formed integral with the enlarged flange or head 14 formed on the end of a plunger 15. The plunger 15 is mounted for sliding movement through anti-friction bearings carried by a housing 16 secured to or formedintegral with the carriage 20. The inner end of the plunger 15 engages the adjacent end of a slide 11 "pivoted at 18 to one arm. 19 of a bell crank. The bell crank 80 is pivoted at 9|- to the carriage and has its other arm 62 in contact with the valve stem .83 of a valve indicated generally by the numeral 84. The valve 84 is enclosed within a valve sleeve 85 pressed into a casing 96'secured to or formed integral with the carriage 29. One end of the pump 98.

other end with the end of the valve plunger 84 tending toyieldably elevate said plunger, as seen in Figure 3. This movement of the valve 84 in an upward direction oscillates the bell crank clockwise about its pivot 8I and through the bar I1 and plunger I5 forces the head II of the tracer arm 88 against the flanged cap I2 for holding the tracer arm 88 in a neutral or horizontal position.

The valve 84 may be termed the primary valve controlled by the tracer arm and in turn controlling the division of flow'of the hydraulic medium to a distributor valve which controls the flow of' the medium to the several motors involved in this invention, as will later appear. As seen in Figure 3, the valve 84 comprises spool portions 89,80 and 9| having between themcannelures 92 and 93. The sleeve 85 is provided interiorly thereof and in alignment with thevalve spool with a circumferential groove 84 of a width slightly in excess of the width of the spool 90. Extending through the sleeve 85' in alignment with the groove 94 are ports 95 in turn aligned with aport 95 through the valve. casing 86. Connected with the port 96 is one end of a conduit or channel 91 which is connected at its other end to the discharge of a The intake of the pump 98 is connected by a conduit or channel 99 to the sump from which the hydraulic medium is drawn.

As was mentioned above, the valve 84 is utilized for controlling the distribution of the flow of 'the hydraulic medium which passes from the valve through the ports Ill0 and- I0l formed in the casing 86 and sleeve 85. The port I00 is connected by a'conduit or channel I02 with the left handend, as seen in Figure 5 of a distributing valve I03 while the port IOI isconnected by a conduit or channel I04 with the right hand end of said. valve. With the spool portion 90 of the valve 84 in -a central position as respects the groove 94 and the valve I03 also in a central position, there will be a substantially equal division of flow of the fluid between the conduits I02 and I04. Under this condition there will be equal pressures on the opposite ends of the valve I03. and thus there, will be no force tendin to move the latter from its central position. S ting of the valve 84 to either the right or left, as seen in Figure 5, disturbs the 'equal division of the fluid and causes more fluid to flow'through one of the conduits l02 and I04 than through the other and thereby shifts the valve I03 to either work.

the right or left of, its .central position, asowill be more fully explained hereafter,

The shifting of the valve'l03 controls the quantity of flow perfunit of time to the hydraulic motors 28 -and 39 to determine therate'sat which they will be operated and consequently the rate at which the work table I2 is moved relative to the cutters andthe rate at which the carriage 20 is moved-to'shift the cutter toward and from the work while operating thereon. In addition, the position of the valve I03 determines whether the :tool moved toward the work or from the q The shifting of the valve 84, and therefore also of the valve I03 is accomplished, as follows:

With. the tracer ball 69 removed-fromcon'tact with the master pattern, the primary valve 84 would be shifted by the spring 88 completely to the left, as seen in Figure 5, so that the maximum flow from the line 91, is through the port IIII and conduit I04 for shifting the valve I 08 casing 86 is closed by a head or cap '81 against to its extreme left hand position. As the tracer which abuts one end of a spring 88 abutting on its I03 is shifted to its extreme right hand position.

The function of the several positions of the valve will be later described.

Hydraulic actuating-force is supplied to the cylinders H and 30 by a pump I06 which has its intake side connected by a suction conduit I01 with the sump 99'. The discharge side of the pump I05 is connected by a conduit I08 with a pair of variable fluid resistances III and H2. The, fluid resistances III and II 2 are formed by tapered spools on a valve plunger 2', see

Figure 15, constructed in such a way that upon movement of the plunger in its sleeve in either direction the fluid resistance of one spool increases as the other decreases thus forming part of a speedcontrol mechanism for determining the speed at'which the parts may be actuated.

The action of (this valve is somewhat described below, but fora complete description thereof see co-pending application of Ernst and Sassen for Balanced pressure hydraulic circuit, Serial Number 490,154, filed October I 21, .1930. The discharge of the pump I08 is thus divided into two portions, the ratio between the two fluid resistances III and H2 determining the proportion of the pump output'which is to be returned direct to reservoir and the proportion which is to be utilized for machine actuation.

In order that the portion of the medium retained for actual use may remain substantially constant regardless of the variations in work resistance that may be encountered, the flow past spool III is connected by. the conduit II8 with one end of the casing.II4 containinga shiftable balance valve III. 'As seen in Figure 5, the hydraulic'medium flowing through theconduit II8 acts on the left hand end of the valve III and would tend to shift the valve tolthe right were it not for the pressure acting on the other end. The right hand'end oi' the valve -is connected 'by'meansfof conduit III to conduit II8 which connects the flow past spool II2 to the port I20, and. through branch line- I22 to the port I23 of the distributor valve I08;

The pressure acting on the right hand end of the balance valve 5 will always be" controlled by the fluid resistances coming after it which includes the workresistance of the motors 28 and 89. This pressure willthus tend to move the valve I I5 "to the left, and in so doing 'prevent flow-taking place through the conduit, II 8. If this were to happen,'the pressure in the line II3 would instantly be raised. in value until it was equal to the pressure inthe line I08, The

latterv must obviously be greater than the pressure -in the line I I6, since there is a. pressure drop due to the throttled flow past spool -II2.

Aeondition of equilibrium can only be obtained by throttling the flow through the tapered end of thebalance valve II5, until the pressure in the line H8 is exactly equalto that-in the line II8.- As a result, the pressure drop across the fluid resistance III is at all same as that across the fluid resistance H2 and consequently for any given setting of the speed con trol valve 2', thedivision of flow is constant. The rate of movement of the motors 28 and 39 will thus be independent of the work resistance they may encounter.

The conduit I I6 terminates at port I20 formed through a valve sleeve I2I that is positioned around the valve I03. A branch pressure line I22 extends from the line H6 and terminates in a port I23 formed in the valve sleeve I2I. Ports I24 and I25 are formed through the valve sleeve I2I respectively adjacent the ports I20 and I23 which form one terminus for conduits or channels I26 and I21 respectively terminating at one end of a balance valve casing I28 and depth valve casing I29, the functions of which will be described in detail later. A port I30 formed through the valve sleeve I2I adjacent the port I23 forms one terminus for a conduit or channel I3I terminating at the depth valve casing I29. A port I32 adjacent the port I30 and formed through the valve sleeve I2I likewise is the terminus for a conduit or channel I33 which has its other end terminating in the reversing valve casing 33. A branch conduit or channel I34 connects the conduit I33 with a second portion of the valve casing 33. The valve sleeve I 2I also has formed therethrough ports I35, I36 and I31 respectively forming the terminus for branch discharge conduits or chan- 'nels I38, I39 and I40 each of which has its opposite terminus connected with the main discharge conduit or channel II9, which terminates in the tank or sump. 99

The balance valve casing I28 encloses a shiftable valve I which controls outlet ports at each end of the casing I26;and from which respectively extend a conduit or channel 44 and a conduit or channel I42. The channel 44 terminating in'the lower end of the cylinder M, as seen in Figure 5, while the channel I42 terminates in the valve casing 33 of the reversing valve 34. Also connected with the valve casing I28 at its right hand end is a conduit I43 which has its other end connected with the right hand end of a second-balance valve casing I44. The balance valve casing I44 encloses a balance valve I45 which is similar to the valve I and.

controls the discharge from opposite ends of said casing through the conduit I43 ,or the conduit 43. nects with the upper end of the cylinder 4|. Connecting ,with the opposite ends of the balance valve casing I44 are conduits I46 and I41 each terminating at their other 'end with the depth valve casing I29.

Shunted between the conduit I41 and conduit 43 is a by-pass conduit I48 containing a check valve I49 whereby discharge fluid from the cylinder 4I may flow from conduit 43 into conduit I41 but the reverse flow being prohibited. Likewise shunted between the conduit 44 and the balance valve casing I26 is a by-pass conduit/I50 having therein the check valve I5I allowing a flow of discharge fluid from the other end of the cylinder 4| .through the conduit 44 into the casing I26,'but prohibiting a reverse flow thereof. J 4

Shunted across the main discharge conduit H9 and the conduit I08 from the pump I06 is a conduit or channel I52 in which is provided an emergency relief valve I53 to permit escape of fluid to the reservoir from the line I08 when the pump pressure exceeds a certain predetermined As was noted above, the conduit 43 con-- maximum. This valvesthus does not come into play during normal operation of the circuit.

The valve I03 as was mentioned above, is axially shiftabie through the sleeve I 2I for which purpose it is provided with piston portions I54' and I55 which also serve as guides for prohibiting any rotative movement of the valve and for which purpose they are received in elongated slots I56 and I51 formed respectively in heads I58 and I59. The heads I56 and I59 being provided with ports I60 and I6I which terminate adjacent the ends of the slots I56 and I 51. Adjacent the piston portions the valve has slightly reduced portions I62 and I63 in which are formed grooves I64. Adjacent the portions I62 and I63 are cylindrical spools I65 and I66 followed respectively by cannelure I61 and slotted portion I66. The valve is respectively provided adjacent the portions I61 and I68, with slotted portion I69 and cannelure .slotted portion I13 and piston I14. The valve;

is then provided with the cannelure I15 next to the portion I13 and a slotted portion I16 adjacent the spool I14. Between the cannelure I15 and slotted portion I 16, the valve from left to right has the slotted portion I11, spool or piston I18, slotted portion I19, cannelure I60, spool I6I, slotted portion I82, and cannelure I83.

As will be later described in detafl, the slotted portions of the valve are in reality reduced portions which act as resistances to the flow of the fluid and determine the amount of flow that passes into the conduits or lines extending from them. As the distributor valve is moved, more or less of the said reduced portions are uncovered and as the reduced portion controlling the flow of the fluid to the motor 39 to effect an infeed, for example, is made smaller the reduced portion controlling the flow of the fluid to the traverse motor 28 is increased. From this it will be seen that the speed atwhich the motors are operated will depend on the increase or decrease of the fluid resistances. Also that as the speed of one motor to thereby accurately reproduce the pattern.

The operation of the device thus far described is as follows: arm ball end is free of the pattern the spring 63 actuates the valve 84 to the extreme left hand position, as shown in Figure .5, which position is As above noted, when the tracer determined by the adjustment of the flange cap 12 on the housing 66, which parts it will be noted from Figure 3, are threaded to one another. This adjustment is made so that a slight flow of fluid is at all times maintained in the conduit I02 for maintaining a slight pressure on the valve piston I 54 although 'the major flow of the fluid is through the conduit I04. with this position of the valve 84, the distributor valve l03 will-.be

shifted to its extremeleft hand position, as seen in Figure '7. At this time, the flow from the pump I06 through the conduit I 06 will, depending upon the desired rate of actuation of the parts, be divided between the conduits I09 and H0, the former discharging to the sump or tank while the latter discharges through the conduit II1. With the valve in its extreme left hand position, as seen in Figure 7, the port I20 will be cut of! by the piston or spool III of the valve so that no flow is had through the conduit I26. The port I25 at this time will be open wide to receive the flow from the branch pressure line I22 by way of the cannelure I80. Also at this time the piston'or spool I14 of the valve I33 will completely close off the-port I30 thereby prohibiting any flow of fluid through the conduit, I3I. The flow of fluid through the port I25 and conduit I21 connected therewith will pass through the depth valve casingI29 and into and through the conduit I41 shifting the balance valve I45 to the right to open the port to the conduit 43 thereby permitting the entire effective flow of fluid into the cylinder ,4I. This will actuate the piston 39 through the cylinder 4I in a direction to cause the tracer arm and cutter to approach the pattern and work respectively. The exhaust from the other side of e the piston 39 from the cylinder 4| is through the conduit 44, by-pass conduit I50, check valve I5I, balance valve casing I28, conduit I28, port I24, grooved portion I13, cannelure I15, port I36 and branch exhaust conduit I38 to the main exhaust conduit I I9 for return to. the tank or sump. This movement of the parts continues until the tracer point 10 engages with the pattern I05.

Upon engagement of the tracer with the pattern the plunger is axially reciprocated to the left, as seen in Figure 3, thereby actuating the valve 84 relative to its casing. Referring now to Figure 5, the movement of the valve 84 is to the right against the resistance of the spring 88. This movement causes the valve spool 90 of.the primary valve 84 to be-shifted relative to the groove 94 within the valve casing to thereby cut down the flow of fluid'through the conduit I04 and increase the flow through the conduit I02.

This change in the flow of the hydraulic medium effects a movement of the valve I03 to the right proportional to the movement of the tracer and primary valve, thereby causing the collar or piston I 14 thereof to uncover the port 130 to initiate the movement of the table while at the same time the collar I18 is cutting off the flow through the port I 25 to slow down the movement of the tracer and tool. Continued movement of the collars or piston portions I14 and I18 of the valve correspondingly increases the flow of the flud through the conduit I3I and decreases the flow through the conduit I21. The decrease in the flow through the conduit I21 slows down the movement of the piston 89 relative to its cylinder while the flow through the conduit I3 I, passing through the. out depth valve casing I29, conduit I40, balance valve I casings I44 and I28 into the conduit I42 increases the rate of movement of the piston 29. Depending upon the position of the reversing valve 34 the fluid in the conduit I42 is connected witheither conduit 3| or conduit 32. As seen in the drawings, the conduit I42 is connected through the cannelure I84 of the reversing valve 34 with the conduit II thereby shfting the piston withinthe cylinder 30 and the table I2 connected therewith to the left. The exhaust from the other, side of the piston isdischarged through the conduit 82 and connected by the cannelure I85 of the valve 84 with the discharge conduitv 33 to the dis- As the tracer deflection increases the distribuw tor valve will move to the position illustrated in Figure 8, at which time the tracer and cutter are actuated toward the pattern -=simultaneous1y with forty-five degrees.

the movement of the table transversely of the tracer and cutter at'equalrates of speed to cut for example, a surface extending at "an angle of This movement of the parts continues until the tracer is further deflected as by a surface that is greater or less than forty-five degrees, which deflection further varies the position of the primary valve and'the flow of fluid through the conduits I02 and I04. As the surface being followed by the tracer approaches a surface parallel to the line of movement of the table, the tracer and primary valveare deflected to a point for varying the flow of fluid through conduits I02 and I04 until the said surface, which is parallel to the line of movement, is reached whereupon the distributor valve is in the position shown in Figure 5, at which time the ports I24 and I25 are completely closed off by the piston or spool portions I1! and I18 of the valve, while the port I is fully open to the conduit I22, the fluid passing through the grooved portion I82, cannelure I83 and grooved portion I10. With the parts in this position no movement is imparted to the slide 20 carrying the tracer arm and cutter, while all movement is imparted to the table transversely of the tracer and tool. If the portion of the pattern engaged by the tracer is parallel with the movement of the table, no furthershifting of the primary valve 84 will take place and consequently no change in the position of the valve I03 will result. If, however, a rise is encountered in the pattern bythe tracer arm necessitating a withdrawal of the cutter or an outfeed thereof, the valve 84 will be still further shifted against the resistance of spring 88. Th's will again unbalance the flow in the lines I 02 and I04 by increasing the flow in the line I02 and decreasing the flow in the line I04. This shifts the valve I03 further to the right to thereby uh:- cover the port I24 to the pressure in l'ne II6 so that a flow of the medium may be had through the cannelure I81, slotted portion I68 to the conduit I28, for initiating a reverse movement of the piston 33' and a slowing-down in the movement of the piston 29.

During the previous operation of the parts the balance valve I was shifted relative to its casing to maintain the proper desired flow through the lines I21 and I3I so that the hydraulic motors for infeeding the tool and traversing the table are operated at proper speeds.

-During this operation the balance valve I is inoperative but upon reverse actuation of the mothe movement of the piston 28. At the'same time the flow-of the fluid through the line I28 is through'the valve casing I28 into the conduit I44 against the opposite side of the piston 88. This will effect a retraction of the slide 20 or a movement thereof to the left, as seen-in Figure 1.

If the rise is in a continuous angular line -with-' out a variation in the degree thereof the tracer arm 88 will be maintained at a definite position at which time no further movement of the valve 84 will take place and consequently no additional shifting of the distributor valv'e I03 will be had. If the surface being cut is on a-forty-flve degree angle the cutter or tool will be actuated from the work simultaneously with .the traverse of the work at equal speeds wherefor the tracer will in Figure 9 for equally distributing the flow of fluid to both of the motors 39 and 28. At this time then division of flow of the hydraulic medium to the cylinders 4| and 30 is maintained so that the cutter is moving outwardly at a given rate while the table is traversing the work relative to the cutter at the same rate, the resultant of which rates of movement is the angle of out being reproduced from the pattern on the work, namely forty-five degrees. The exhaust from the upper end of cylinder M, asseen in Figure 5, is by way of conduit 43, by-pass conduit I48, check valve I49, conduit I41, depth'valve casing I29, conduit, I21, port I25, grooved portion I11, cannelure I15, port I38 and branch exhaust conduit I39 and the main exhaust conduit I I9 to the sump.

If the tracer engages a rise or obstruction on the pattern such as a wall, for example, projecting substantially straight outwardly, the valve 84 will be shifted to its efireme right hand position and thereby shift the istributor valve to its extreme right hand positiort illustrated in Figure 10. At this time the spool or piston portion I8! and the spool or piston portion I18 respectively cut off the flow to theconduitsPISI and I21 while the grooved portion I69 and cannelure I61 connect the medium with conduit I26, thereby stopping the movement of the table I2 while. effecting the outward movementof the carriage 20.

In the operation of the machine the work table is traversed relative to the tool and tracer arm.- At each end of the reciprocatory stroke of the table I2 the reverse valve 34 is actuated. For this purpose the valve stem 35 has secured toit a load and fire mechanism indicated generally by the numeral I86 which is ofweil known construction and needs no further exp anation here. The load fand fire mechanism is v tuated by a vertical plungen lfl carried by the support I I, the plunger having projecting from its. tongue I88 adapted to lie in the path of movement of adjustable reversing dogs I89 and I90adjustably secured in theusual T-slot I9I formed quired for the reversing in the forward face of the table I2. During the interval of time reof the valve by the dogs J89 or I90, as above described, the tongue or lug 65 projecting from the rear of the table engages with one of the dogs 66 or 61 on the rod 62 for actuating the bell crank I60 and thereby through the pawls 54 or 55 increnie tally rotating-the ratchet 53 and shaft as was above described. The incremental rotation of the shaft .5I simultaneously rotates the screw 46 for thereby vertically adjusting the slide I8 relative to the column I5 so that the cutter and tracer are positioned for the next traverse thereof relative to the pattern and work. :It isilhelieved that ;this operation of the machine is readily understood from the drawings. I From the foregoing it will be noted that the sliding of the distributor valve, past the several ports, in the valve sleeve, through the slotted portions of the valve, effects the proper distribution of flow of the fluid to the motors for actuating said motors at different independent rates to thereby vary the line of cut on the work in accordance with the inclination of the pattern. This distribution of thehydraulic pressure, it will be noted, is maintained by the balance pressure valves MI and I45 which shift as the flow to the opposite ends thereof varies. In the event a creeping tendency is had by either of the motors, which is not in accordance with the setting of the valve I03, the pressure on the ends of the balance valve would become unequal and the resultthe possible movement 'of pattern essary to finally bring ant higher pressure on the one side thereof would shift the valve and thereby again balance the flow through these valves and rectify any creeping or over-running tendency of the motors.

In the cutting of deep dies, .it is impossible for the cutting tool to be sunk to the necessary or required depth to remove all of the material from the die cavity during a single pass of the tracer and tool relative to the pattern and work. It therefore becomes necessary that the material from the die cavity be removed in layers or steps. In the past this was accomplished by providing a plurality of dies each of a different depth so that the machine couldbe properly controlled while reproducing each successive portion of the die. By this invention it'is not necessary to provide a plurality of patterns, as automatic means are included for limiting the depth of cut that can be made during a single reproducing operation. To this end the depth out control valve was provided closed therein the valve plunger I92 having spool portions I93 and I94 forming the cannelure I95. As seen in Figure 1, the valve casing I29 is carried by the carriage 20 having the plunger I92 projecting from the end thereof. In the line of movement of the carriage 20 the slide I8 has an abutment in the nature of an adjustable screw I96 extending through a lug I91 on the slide I8. A

spring I98 is enclosed within the casing I29 and abuts an enlarged headed end I99 of the valve for shifting it to its normal position, as seen in Figure 5.

The slide carrying the tracer and cutter may be fed into the work until the abutment I96 engages with the plunger I92 which shifts the valve against the yielding resistance of spring line or conduit I21 with the conduit I46 and disconnect the line I21 from the conduit I41 thereby cutting off further movement of the piston 39' while permitting an unrestricted movement of the piston 29 to thereby cause the table to traverse the work relative to the tool without regard to the tracer and cutter slide as they are held against substantially im- I98 to connect the f movable abutments. Continued movement of the parts will eventually again bring thetracer and the valve 04 will be shifted for again shifting the distributor valve I03 and thereby retracting the carriage 20 so that the parts will again be under control of the primary valve 84. The tracer, work, pattern and tool are actuated relative to one another a plurality or times or the cycle of operation of the machine is repeated as often as it is necthe tracer into contact with the bottom of the pattern whereupon the die will be a complete and faihiul reproduction of the pattern without the use ated patterns. I

In the modification shown in Figure 6, a single pump-200 is employed instead of the pumps line .20I to the sump and discharges through a conduit 202 connected with a pair of branch conduits or channels 203 and 2.04-respectively terminating in the complementary variable fluid resistances' 295 and 206. The flow past the resistances 15' connected to opposite ends fof 'a balance valve casing 201 which encloses the valve 208. Extending from the casing 201 are conduits or channels 209 and 2I0, the latter extending to the tank or sump for returning the hydraulic medium not needed for the operation of the parts. The balance valve 208 and adjustable fluid resistances of a plurality'of graduinto conta'ct with oneanother whereupon 98 and I00. This pump is connected by a suction 205 and 206 constitute a rate controller for settingor adjusting the ultimate rate of flowof the hydraulic medium and determines the speed at which the parts are operated. and takes the place of the valvel I5 and resistances III and H2 disclosed in the circuit in Figure 5. For a complete description of their operation attention is invited to the description above and the co-pending application referred to in connection with the speed control parts of Figure 5.

The lineor conduit 209 terminates at a transverse conduit or line 2 to the ends of which are connected fluid resistances M2 and 2I3, which may conveniently consist of lengths of small bore tubing or the like and which respectively terminate at the upper and lower ends of a balance valve casing 2. The casing 2M encloses a valve 2I5 which regulates and controls the discharge from the casing 2 I4 through the conduits 2I6 and 2 H. The conduit 2I6 terminates in the primary valve casing 86 and is similar to the conduit 9'! of Figure 5. The conduit 2" connects with the pressure line I I6 01' the circuit shown in Figure 5 and supplies the fluid that is utilized for shifting the pistons 29 and 39', as above described.

The balance valve 2I5 is acted upon on opposite ends thereof by the pressures developed by the fluid resistances 2I2 and 2I3 and takes up a position in accordance with these pressures acting on said opposite ends. The pressures at the said ends of the valve are not only dependent on the fluid resistances 2| 2 and 2I3, but alsi'ron' the work resistance encountered in the lines 2I6 and 2" as well as the resistance of the parts operated by the fluid in said lines H6 and 2". From this it will be seen that a variation in pressure at either end of the valve would cause it to shiftits position toward the end of least pressure and thereby decrease-or cut down the flow past this end of the valve and thereby increase the pressure at said end of the valve. This shifting of the valve would build up the pressure at that end of the valve toward which it is moved until the pressures at each end of the valve are equal and the valve is again held in equilibrium. In this manner the flow through the lines or channels 2I6 and 2|! is maintained, which flow is in accordance with the fluid resistances 2I2 and 2I3 and the setting of the speed controller which includes fluid resistances, 205 and 206. For a more complete description of the balance valve for maintaining the pressure in two motors or pressure lines, attention is invited to the copending application of Hans Ernst for Multiple hydraulic motor operation, Serial Number 614,980, filed June 2, 1932.

It should be noted that the difierence between the size of the groove 94 and the width of the collar is but a small amount and in fact there is but a fewthousandths of, an inch difference in their widths. From this it will be seen that comparatively high resistances are ofiered at 225 and 226 Figure 5 to the flow of the hydraulic medium even with the valve in its central position and with equal openings between the sides of the groove and the sides 01' the collar. I

As shown in Figures 5. and 11' valve heads I58 and I50 are each respectively provided with a slot I56 and I51 in which is received the tongue portions I54 and I55 01' the valve. Centrally of the heads they are each provided with an enlarged bore 2 I0 communicating through the radial ports I60 and I6I with grooves 2I9 and 220 respectively exteriorlv of each of the heads I58 and I59. Communicating with the grooves 2I0 and 220 respectively, are the ports 22l, to which are respectively connected the conduits I02 and I00.

In order for the fluid to pass from the valve casing 86 into the conduits I02 and I04 and into and from the chambers I56 and I51 respectively provided at the left and right hand ends of the distributor valve, it must flow through the fluid resistances 225 and 226 and fluid resistances I62 and I63, respectively formed by the'grooved portions bearing the same reference numerals at the left and right hand ends of the valve. These resistances vary with the movement of the valves, thus when the valve 84 moves to the right, as seen in Figure 5, the resistance 226 increases and the resistance 225 decreases, or whenthe valve is at its extreme left hand position, as shown in F lgure 5, the resistance 225 is at a maximum and the resistance 226 is at a minimum and conversely when the valve 84 is at its extreme right hand position the resistance 225 is at a minimum and the resistance 226 at a maximum. Also when the distributor valve I03 is at its extreme left hand position as shown in Figure "I, the resistance I62 is at a maximum and the resistance I63 is at a minimum, while when the distributor is in a substantially midway position, shown in Figure 5, these resistances are substantially equal. When the valve I03 is in its other extreme position, that is, to the right, as shown in Figure 10, the resistance I62 is at a minimum with the resistance I63 at a maximum. The flow of the fluid through each of the conduits I02 and I0 must therefore pass through two /variable fluid resistances which are in serial rel ation to each other.

The portions of the distributor valve described as slotted portions are in reality reduced portions as compared with their adjacent enlarged piston portions, see Figures 12 and 13, the former being an enlarged sectional "view through one of said slotted portions and the latter being an enlarged elevational view thereof and it is deemed suflicient if but one of said portions be described in detail. Accordingly, having particular reference to Figures 12 and 13, the spool or piston portion of the valve is substantially the same diameter as the bore through the sleeve while the slotted or reduced portion adjacent thereto is slightly smaller in diameter, which difference in size is in the nature of but a few thousandths of an inch on the radiusthereof. 'By this construction a channel I 64 of a width equal to'the difference betweenthe radius of the reduced portion and the radius of the bore through the sleeve is formed, which channel acts as a resistance to the flow of the hydraulic medium to and through the ports with which it is aligned. As seen in Figure 12, there are provided four ports throughithe valve being equally spaced from one another and by referenceto Figure 13, it will be noted that the length of the reduced portion is greater than the largest dimension of the ports. From this it would follow that the resistance would be the oriflce formed around the-reduced portion and valve sleeve and this resistance would be substantially unvaried as the valve is shifted, unless the end thereof passed the ends of the ports. For this reason the reduced portions are provided with end mill slots or grooves 222 which convey the medium from the cannelure adjacent the end of the reduced portion, and the resistance to the flow from the ports is formed by the channel disposed circumferentially of the reduced .portion of the valve between the end mill slots and the 15 fluid resistances 225 and 226 will have fixed values,

Ports. From this it will be seen that as the reduced portion is shifted relative to the ports the channel is increased in length for thereby varying the resistance to flow of the medium through the ports. As will be noted in Figure 12, the reduced portion of the valve is provided with end mill slots 222 in such a position as to be disposed intermediate adjacent ports so that the groove or slot will feed one of a pair of ports. In order that the flowing pressure through and from the ports is equal the valve sleeve is provided exteriorly thereof with a circumferential groove for connecting the said ports, as is usual practice. From the foregoing it will be noted that regardless of the axial position of the valve as respects the sleeve the same thickness of channel is at all times maintained, but as the reduced portion passes the'ends of the ports, the length of the channel varies. In practice it has been found that with this type of valve the influence of the viscosity of the oil on the flow thereof is substantially equal at all points of adjustment of the valve whether the channel is of a great or a small length. Consequently, the relationship between the various fluid resistances remains the same regardless of changes in viscosity of the oil caused by temperature changes during practice, or by the use of different hydraulic'mediums.

In order more fully to comprehend the action of this device, attention is invited to a condition where fluid is being positively forced through a stricture or fluid resistance, which may consist of an orifice or passage of small cross-section, at a given rate of flow. There will then be built up,

at the point where the fluid enters the resistance,

a pressure, which is a function of the rate of flow and the ability of the resistance to impede or resist flow.

This pressure may be increased by the following three methods:-

(a) by increasing the rate of flow without changing the resistance.

(b) by increasing the resistance (such as by reducing the area of the orifice or passage without changing the rate of flow).

(c) by increasing the viscosity of the hydraulic medium, without changing either the resistance or rate of flow.

A unit of fluid resistance may now be set up, which consists of the resistance to flow encountered by the passage of unit quantity in unit time at unit pressure. Such a unit will in all respects be similar to the electrical ohm and use may be made of a relationship, equivalent to Ohms law, which may be written as follows:

Where P represents the unit pressure, Q is the rate of now of unit quantity in unit time, and R is the resistance in units of resistance for a given fluid already under pressure, which may be maintained at 'a given value by providing a second resistance. which permits the escape of fluid entering through the first resistance, thenthe pressure ahead of the latter, will have a value equal to the pressure in the second chamber, plus the pressure built up by the flow through the first resistance. The value P in the expression P=QR, may thus be made to represent the pressure drop across a resistance.

For any position of thepriniary valve 84, the

, through 225:-

assuming that the temperature of the hydraulic medium, and therefore its viscosity, is constant. Since friction is a negligible factor, due to the high pressure film lubrication aiforded by the hydraulic medium, the valve I03 is freely slidable in its sleeve. Whenever the pressures in the lines I02 and I04 are unequal, therefore, there will be an unopposed resultant force acting on the piston areas formed by the ends of the valve. Under such conditions,-the'valve will thus be forced to move towards the end where the lowestpressure is present and, as previously explained, such movement will immediately cause an increase of the resistance at that end, and 'a complementary decrease in resistance at the other end. This in turn will cause the lower pressure to be increased, and the higher pressure to be decreased.

A position of equilibrium will thus be attained when the two pressures are substantially equal. When this is the case, the pressure drop across the resistances 225 and 226 willbe equal, and that across I02. and I63 will likewise be equal.

If now the pressure in the line 91 is represented by P1, and that in the lines I02 and I04 (now being equal) by P2, and the resistance to flow through 225 by R1 units of resistance, and through 226 by Rs units'of resistance, then the flow and the fiowlthrough 226:-

P P Q2= whence Q1R1=QeRs 1 All of the flow that passes through the resistance 225 is compelled also to pass through the resistance I62, since it has no otheroutlet. The flow through I62 is thus also Q1 and if the resistance to flow at this point is R: units of resistance, and assuming the pressure in the line I38 to be zero, then:

Similarly. if a. is the resistance through I63 111 similar units of resistance:-

Q2 whence I Q1 a=Q2 4 (2) Combining the equations (1) and (2) we finally obtain the relationship:-

R; R; .It will be noted that the various fluid resistances consist of long, narrow slits. It has been shown by experiment, that the resistance of such orifices is substantially directly proportional to the viscosity of the hydraulic medium. If the I temperature of the system is thus changed, resulting in a change in the viscosity, the above relationship will remain unaffected; since such a change will affect the numerator and the denominator of the two fractions equally.

From the foregoing it will be seen that for any given position of the primary valve 84 the distributing valve I03 will automatically take up'a corresponding definite position relative to its enclosing sleeve; The position of the'distribu'torvalve will be such that the ratio of the resistances I62 and I63 is always equal to the ratio of the valve from this position will automatically cause unequal pressures in the chambers I56 and I51 which'in turn' will automatically restore the valve to-its correct position. However, in order that the movement of I the table I2 and the carriage may be controlled by a minute movement of the tracer 69. the system should preferably be designed so that the valve I03 will be moved from its extreme left hand position to its extreme right hand position upon only a very small movement of the valve 64. This isfaccomplished by constructing the distributor valve I03 in such a way that it must be moved a much greater distance than the primary valve 64 in order to make the same change in the ratio between the resistances I62 and I63, as is made in the ratio between the resistances 225 and 226; thus a very slight move-. ment of the primary valve 64 effects a large movement of the distributor valve I03. between the movements may thus be a few thousandths of an inch of movement of the primary valve for an inch or more of movement of the distributor valve; or of the order of several hundred to one. It is to be understood that this is by way of example only as'the ratio may be of any desired value. From this it will be seen that the primary valve is extremely sensitive and that only a very slight movement of the latter is necessary to obtain a large movement of the distributor valve, the combined resistances I62 and I66 and 225 and 226, however, effecting a very accurate control of both the primary and distributor valves in accordance with the contour of the pattern being reproduced. It will also be noted that a very simple and eil'ective hydraulic amplifying mechanism is thereby provided.

It will be noted that the return flow from the traversingmotor 26 must passthrough the resistances I12 and I66 in serial'relation to each other in order to escape to the reservoir. When the valve 103 is at either end, as in Figures 7 and 10, the resistances I68 and I12 will alternately have, theoretically, an infinite value. As these resistances are in' serial relationship the return flow from this .motor' will then be com pletely blocked, thus positively preventinganytendency to coast or over-rim. In' all other positions of the valve I03, this further serves to maintain a back pressure on the motor 26 to insure a smoothly controlled movement under all operating conditions.

In Figure 17 there is shown the mechanism utilized for set up purposes and to manually control the-operation of the machine. As there shown, the distributor valve operating lines I02 and I04 instead of going directly to the ends of the distributor valve pass through a supplementary valve 250 that is enclosed within the'usual valve casing l. The valve itself may beprovided with piston portions252, 253, 254, 255 and 2 56 forming between each pair a cannelure. The cannelure 251 between the piston portions 252 and 256 directsthe medium from the line I02 into-a conduit 256 which terminates at the left' hand and of the distributor valve casing. The line 256 is therefore a continuation of the line .I02 with the valve 250 disposed between them. The cannelure 259 formed between piston portions 253 and 254 connects the line I 04 with the conduit 260 which terminates at the right hand end of the distributor valve. This conduit 260 is there-' fore a continuation of the conduit I04 with the valve disposed between them. 1

The pump line-such as 202 in Figure 6, or 61 The ratio in Figure 5, has extending from it a branch pressure line 26I which terminates at its other end in an elongated port 262 formed in the casing of a manually controlled valve 263 that functions the same as the primary valve 64 except that con-. siderably more movement must be imparted to it than the primary valve 64 to obtain the same result. The valve 263 serves the function of controlling the flow of pressure to the opposite ends of the distributor valve during setting up and when manually actuating the machine. This valve 263 is enclosed within a suitable casing 264 and the valve has formed thereon end piston guide portions 265 and 266 from which the reduced stem portion 261 extends. Intermediate the piston portions 265'and 266 the stem is provided as at 266 with an enlarged collar from opposite sides of which conical valves 266 and 210v portion 266 and central enlarged portion 266.

Extending from these chambers are conduits or lines 215 and 216 which respectively terminate at the valve casing 25I and respectively empty into the cannelure 211, formed between the piston portions 254 and 255, and the cannelure 216, formed between the piston portions255'and 256.

The valve 250 is adapted to be axially reciprocated to the right from the position shown in Figure 17. Movement of .the valve is accomplished by means of thelever 21.6 pivoted at 260 intermediate its ends and having-a pin and slot connection 26I with the valve 250. Oscillation of the lever 2.19 in a clockwise direction-will axially shift 1 the valve to break the connection between the conduits I02 and 256 andI04 and 260 and dispose the branch conduits 262 and 263 in registry with cannelures 211 and 216. The conduits 262 and 263 respectively connect with conduits 256 and 260 and since the conduits 215 and 216 are in registry with the cannelures 211 and 216, the shifting of the valve will through the cannelures211 and 216 respectively connect the lines 215 and 262 and lines 216 and 263. The distributor valve will -'under these circumstances be actuated by the division of flow effected by the valve 263 and bydraulic pressure passing through the line 26 I. In order to shift the valve 263 it is'connected by means of a pin and slot connection 264 with a lever 265 pivoted at 266 intermediate its ends. As above described movement of the valve 266 will vary the resistances on each side of the enlarged central portion 266 ofthe valve for varying'the amount of flow through lines 215 and 216 and in accordance with the above description this flow, determinesthe position of the distributor valve and consequently the rate and direction of movement of the hydraulic motors controlling the machine parts. a

From the foregoing it willbe noted that there has been provided a valve which will connect the distributor valve with the hydraulic pressure source for either manual control of said valve or automatic control thereof by means of a pattern or other master.

'In order to very or adjust the speed of opera- I aooassv tion of the machine, the speed control mechanism includes a valve member ll! having the inclined conical portions 2 and III that co-operate with the conduits lit and H3 and portsat the end thereof for determining the quantity of flow therethrough and consequently the portion which will be returned to reservoir. The valve H2 is enclosed within a valve casing 2 which in addition may have disposed. therein a spring "I tending normally to shift the valve to the left, as seen in Figure 15. In order to limit the movement of the .valve under the influence of the spring and to definitely position same, the va'lve is provided on its free end with a head 29! adapted to engage with the periphery of an eccentric cam 203 keyed machine and, as seen in Figure 16, may have secured to it intermediate its ends a bevel gear 2!! in mesh with a pinion 296 secured to a shaft 291 which extends beyond the end of the table support ll. Secured to the projecting end.of the shaft 291 is a lever 2" having in one end thereof a spring loaded detent 280 co-operating with a serrated plate ill for locking the parts in-their adjusted positions. From this it will be seen that operation of the lever 29. about the axis of the shaft 291 rotates. the setting cam 293 to position the valve 201 relative to its casing and thereby eifect the proper proportioning pf the hydraulic medium from the line ill to the lineal i3 and Ill.

In order to stop the movement of the motors, the valve 281 is adapted to be shifted against the resistance of the spring ill fOrcompIeteIy-shut- =ting off the flow through the conduit H8 and directing the entire flow through the conduit Hi. It is frequently desired to stop the movement of the motors or the machine without changing the feed setting of the .valve 281 or in other words without disturbing the setting of the cam I. For this reason the shaft ill has loosely journaled thereon a sleeve "I to one end of which is secured a cam 302 while to the other end thereof is secured a bevel gear 303. The gear 303 is in -mesh with a complementary bevel gear 3 secured to a shaft 3". The shaft 305 extends "parallel with the shaft 291 and beyond the end of the table support II. The extending portion of this shaft has secured to it a lever 3 adapted to have two positions, one shutting off the flow of the mediumthrough the conduit H8, and the other for permitting the valve to take a position in accordance with the setting of the cam I. These two positions may be readily determined by means of stop pins 301 and ll! between which the lever 306 is movable.

In order to manually reverse the reversing valve 34 from the end of the machinewhere theother control levers are located, the plunger I, which ,co-operating with the dogs I89 and I automatibed and support so that the machine may be readily manually operated without the automatic feature, that the work and pattern supporting "table may be manuallyreversed, the in and out feed of the tracer and tool manually reversed, and

that thespeedofthese parts'maybemanually controlled.

-In order to vary the relative positions of the cutter and tracer, the cutter spindle 22 maybe conveniently-disposed in a quill Ill adapted to be shifted relative to the housing 23 by means of the hand wheel SIS. This adjustment of the quillwill take care of horizontal adjustments between the cutter 2i and tracer 69 so that either may be projected beyond the other or aligned withrone another.

. To vary the axial approach of the cutter and tracer, the motor 24 and the spindle mechanism may be mounted on a subslide Sit for movement relative to themain slide it. This relative movementbeing .eifected by means of ascrew 3|! having a threaded connection with the slide 6 and operated by'a hand wheel Ill.

It is believed from the foregoing description that the complete automatic and manual control of the improved hydraulically operated die sinker I should be readily understood.

What is claimed is:

1. In -'a pattern controlled milling machine the combination with a bed, of a. tracer, a pattern, and a cutter carried by the bed and adapted for relative movement, an hydraulic motor for effecting said movement of the parts in one direction, a second hydraulic motor for eflecting the movement of the parts in an angularly related direction, a primary valve shiftable by the tracer in accordance with variations in the pattern, and a distributorwaive operable by the primary valve to a position correspondlngto the position of the tracer controlled valve for directing pressure to the motors.

2. In a pattern controlled milling machine the combination with a bed, of a tracer, a pattern, and a cutter carried by the bed and adapted for relative movement, an hydraulic motor for effecting said movement of the parts in one direction. a second hydraulic motor for effecting the movement of the parts in an angularly related direction, a primary valve shiftable by the tracer in accordance with variations in the pattern, a distributor valve operable by the primary valve to a position corresponding to the position of the tracer valve for directing pressure to the motors,

-and means operable by the movement of one of the parts for eii'ecting a relative movement there-- of in a third direction.

3. In a machine tool organization of the class described including a pattern, a tracer, and a tool adapted for relative movement, the combination of a pair of hydraulic motors for eifecting thesaid movements, a 'valve for variably controlling the flow of an hydraulic medium between the hydraulic motors whereby a continuous operation by the motors either individually or jointly is had for shifting the parts, and means operable to definite positions'by the tracer in accordance with the variations in the pattern for correspondingly positioning the valve. a.

4. In a machine tool organization of the class described including a pattern, a tracer, and a tool adapted for relative movement, the combination of a pair of hydraulic motors for effecting thesaid movements, a valve for variably controlling the flow,of an hydraulic medium to the hydraulic motors .whereby a continuousoperation of the motors is had for shifting the parts and means operable todeflnite positions by the tracer in accordance with the variations in the. pattern.

for correspondingly -positioning the valve, said -means including a primary valve operable in one flow of the medium therethrough, said resistances being complements of one another in each valve and the resistances of one valve bearing a defl-' nite ratio to the corresponding resistances of the other valve.

13. In a mec of the class described the combination with a tracer, a pattern and a tool adapted to have certain movements imparted thereto, of hydraulic motors for effecting said movements at desired rates, an hydraulic medium for actuating said motors, a distributor valve for determining the distribution of the flow of the hydraulic medium to said. motors, a primary valve for directing the medium to the distributor valve for effecting its relative positions, and means including the tracer for shifting said primary valve in accordance with the variations in the pattern to thereby shift and position the distributor valve.

14. In a mechanism of the class described the combination with a tracer, a pat em and a tool adapted to have cert move ents imparted thereto, of hydraulic otors for eifecting said movements at desired r tes, an hydraulic medium for, actuating said mdtors, a distributor valve,

foPdetermining the/distribution of the flow of the hydraulic medium to said motors, a primary valve for directing the medium to the distributor valve for effecting its relative positions, means including the tracer for shifting said primary valve in accordance with the variations in the pattern to thereby shift and position the distributor valve, and means between the distributor valve for actuating said motors, a distributor valvefor determining the distribution of the flow of the hydraulic medium to said motors, a primary valve for directing the medium to the distributor valve for effecting its relative positions, means including the tracer for shifting said primary valve in accordance with the variations in the pattern to thereby shift and position the distributor valve, and means between the distributor valve and primary valve whereby any movement or adjustment of the primary valve simultaneously moves and adjusts the position of the distributor valve so that for any given position of the-primary valve the secondary valve takes up a definite positcn, said means comprising fluid resistances associated with the primary valve and secondary valve in serial relation to one another.

16. In a mechanismof the class described the combination with a tracer, a pattern and a tool adapted to have certain movements imparted thereto, of hydraulic motors for eifecting said, movements at desired rates, an hydraulic medium for actuating said motors, a distributor valve for determining the distribution of the flow of the hydraulic medium to said motors, a primary' valve for directing the medium tothe distributor valve for effecting its relative positions, means including the tracer for shifting said primary valve in accordance with the variations in the pattern to thereby shift and position the distribu tor valve, and means between the distributor valve and primary valve whereby any movement or adjustment of 1 the primary valve simultaneously moves and adjusts the position of the distributor valve so that for any given position of the primary valve the distributor valve takes up a deflnite'positionfsaid means comprising fluid resistances associated with the primary valve and secondary valve in serial relation to one another, the ratio of the resistances of the primary valve being equal to the ratio of the resistances ofthe secondary valve so that any variation in pressure controlling the movement of the distributor valve will immediately effect a -re-adjustment thereof to its proper position.

; 17. In a mechamsm of the class described the combination with a, pattern, a tracer and rotating tool adapted for movement relative to one another, of a plurality of hydraulic motors for effecting said movements in desired directions and at desired speeds, an hydraulic medium for actuating said motors, a shiftable distributor .valve for controlhng the flow of the medium to the motors and determining the direction of movement thereof, the valve being adapted to be shifted by the hydraulic medium acting on the opposite ends thereof, a primary valve for directing'the flow of the medium to the opposite ends of said distributor valve in difierent quan-' tities, fluid resistances associated with the primary valve and distributor valve for controlling the flow to the ends of the distributor valve, and connections between the primary valve, tracer and pattern whereby the position of the valve is varied in accordance with the contour of the pattern for controlling the flow of the medium which through th resistances associated withthe primary (1 distributor valve instantaneously and automatically controls the position of adjustment of the distributor valve for varying the operation of the hydraulic motors.

18. In apattern" controlled milling machine having a tracer, a pattern, and a-cutter adapted for relative movement, the combination of a pair of hydraulic motors foreflectlng said movement, an hydraulic medium for actuating the motors, a primary valve operatively associated with the tracer and shiftable by the tracer upon deflection of the tracer by the pattern, a distributor valve shiftable to a position corresponding to the position of the primary valve deflection for controlling the flow of the medium to the motors.

19. In a pattern controlled milling machine the combination with a-trac'er, a pattern, a tool and a work support adapted tohave relative movement imparted thereto, of hydraulic motors for eifecting such movement, hydraulic circuits" for controlling the operation of the hydraulic motors including a distributor valve, and con nections between 'the distributor valve and tracer whereby'movement of the tracer by the pattern eifects a proportional movement of the dhtrib- "5 utor valve throughout the range or movement of the tracer.

20. In -a pattern controlled milling machine the. combination with a tracer, a tool, a pattern and a work support adapted for relative movement, or hydraulic motors for eflecting said movement, hydraulic circuits for controlling the movement of the motors and includins a distributorvalve adapted to be hydraulically actuated, a primary valve operable on deflection oi! the tracer ior effecting the movement of the distributor valve in accordance with the movement.

of the tracer, a manually actuable valve in the circuit for eilecting a movement of the distributor valve, and a valve for connecting either the tracer control valve or the manually actuable valve with the distributor valve.

21. In a pattern controlled milling machine the combination with a tracer, a tool, a pattern and a work support adapted for relative movement, of hydraulic motors for eilecting said movement, hydraulic circuits for controlling the movement of the motors and including a distributor valve adapted to be hydraulically actuated. a primary valve operable on deflection oi the tracer ior eilecting the movement of the distributor valve in accordance with the movement oi."

the tracer, a manually aetuable valve in the circuit for effecting a movement or the distributor valve, a valve for connecting either the tracer control valve or the manually actuable valve with the distributor valve,

manually actuable means for axially positioning the cutter and'tracer relative to-one another. 22. In a pattern controlled milling machine the combination with a tracer, a tool, a pattern and a work support adapted for relative move ment, of hydraulic motors tor eflecting said movement, hydraulic circuits for controlling the movement of the motors and including a distributor valve adapted to be hydraulically actuated, a primary valve operable on deflection oi the tracer for efiecting the movement of the distributorvalve in accordance with the movement or the tracer, a manually actuable valve in the circuit i'or eflecting a movement oi the distributor valve, a valve for connecting either the tracer control valve or the manually actuable valve with the distributor valve, manually actuable means for axially positioning the cutter and tracerrelative to one another, and manually operable means for effecting an. axialapproach of the cutter and tracer.

23. In a die sinking machine oi. the class described the combination with atracer, a pattern, a tool and a work support adapted. for relative of the motors and adapted to be hydraulically adjusted, a manually operable positioning valve for .eflecting and determining the position of the distributor valve, and manual means for eflecting the operation of the positioning valve.

24. In a fluid control system, the combination or a volumetrically constant sourg oifluid pres-v sure, branch conduits leading therefrom, fluid resistance means for diversely impeding the rate oi. now to said branch conduits for causing a conduits for actuation by the reduced pressures thereimadditional serially arranged fluid resist-' predetermined pressure drop therein, opposed pistons connected respectively to said branch ances in each conduit for impeding the rate 0! exhaust flow therefrom and thus modifying the respective reduced pressures in the conduits whereby the resultant pressures in the conduits will be equal when the ratio of said serial resistancesisequaltotheratiooitheiirstnamed resistances, a controller connected with the flrst named resistance means, a controlled part, con-' nectedwithsaidserialresistancesandwithsaid' pistons whereby any movement of the con- .troller connected resistances will cause a proportionate movement of the controlled part and associated resistances through said pistons,

said movement continuing until said serial resistances equalize the pressure in said conduits.

25. In a fluid control system the combination with a-volumetrically constant source of fluid pressure, oi branch conduits leading therefrom, a fluid resistance in each conduit, said resistances having a predetermined ratio therebetween, a second fluid resistance in each conduit having a ratio equal to the flrst named ratio .whereby the pressures in said conduits are equal, and means automatically operable upon change in the ratio or the first named resistances to cause a corresponding change in the ratio of the remaining resistances whereby the pressures in saidalconduits will automatically be maintained equ 26. In a fluid .control'system the combination with a volumetrically constant supply of fluid pressure, or branch conduits leading therefrom, interconnected means for establishing a fluid resistance in each branch having a predetermined ratio, additional interconnected means for establishing an additional serial fluid resistance in each channel having a ratio equal to the first named ratio whereby the'conduitpressures will be equal, and meansautomatically operable upon ratio variation of one pair of interconnected rein the other pair of interconnected resistances whereby the ratio of the second pair of fluid resistaiices will always be maintained equal to the ratio of the flrst pair of fluid resistances.

' 27. In a fluid control system the combination of a volumetrically constant supply 0! fluid pres sure, a pair or branch conduits leading therefrom, a variable fluid resistance in each conduit interconnected for simultaneous adjustment to establish difl'erent ratios therebetween, an additionalvariable fluid resistance in each branch conduit interconnected for simultaneousadjustment to a ratio equal to the ratio or the flrst named variable resistances to cause thereby equal pressures in the conduits, means to adjust the flrst named variable resistances to a new ratio and thus eflect press'ural changes in the respective conduits between the resistances therein, and means to utilize the pressural changes to vary said additional resistances to such an extent that they will equalize the pressure in said channels.

28. In a mechanism for transmitting proportionate movements from a tracer to a part conpressuresinthechannelaandmeansresponsivel to a pressure differential in said channels caused by inequality between the ratios of the respective pairs of resistances to re-equalize said ratios.

29. In a motion transmitting mechanism the combination with an actuator and an actuated part, of a pair of fluid channels extending from oneto the other, means to maintain a constant flow through said channels, individual means associated with the actuator and with the actuated part to establish equal pressures in said channels, said means associated with the actuator being adjustable therewith to create a pressure diflferential between said channels, and means responsive to said pressure differential to eiIect movement of the actuated part and the means associated therewith until said difierential is eliminated whereby for a given movement of the actuator a corresponding movement will be efiected in the actuated part.

30. In a mechanism of the class described, a controller part, a controlled part, a pair of hydraulic channels extending from one part to the other, a source of fluid pressure for supplying said channels, fluid resistance means associated with the first part and co-operating fluid resistance means associated with the second named part eflective to establish equal fluid pressures in the channels which is less than the supply pressure, said first resistance means being adjustable by movement of the controller part to unbalance the pressures in said channels, and means responsive to said pressure diflerential to cause continuous movement of the controlled part and variation of the resistance means associated therewith until the pressure diiferential is eliminated.

31. In a device of the class described, the combination of a controller member and a controlled member, a pair of fluid channels extending from one to the other, a source of pressure fluid for supplying said channels, means associated with the controller member for decrementally and incrementally changing the respective pressures in the channels in accordance with its movement, means responsive to said pressure changes to effect movement of the controlled member in accordance with the amount of said pressure differential whereby the members will be maintained in synchronized relation with one another.

32. In a device of the class described for maintaining a synchronized relation between a controller member and a controlled member, the combination of a pair of fluid channels extending between the members, means associated with the controller to eifect a pressure difl'erential between said channels in accordance with its movement, and means responsive to said pressure differential to effect movement of the controlled. member in an amount depending upon the amount of saidpressure difierential whereby predetermined movement of the controller will effect a corresponding predetermined movement in the controlled member.

33. In a motion transmitting system, the combination with a controller. member and a controlled member, of a pair of fluid channels extending from one to the other, a source or fluid pressure for supplying said channels, pressure difierential creating means associated with the controller member and effective upon 'ygradual movement thereof to efiect a gradual change in the pressure differential between said channels, there being a definite gradation for each position of the controller member, a pressure differential varying means associated with the controlled member and responsive to a pressure differential in said channels created by the controller member for correspondingly moving the controlled member an amount necessary to reduce the pressure differential to zero and thereby take up a position in synchronized relation to the position of the controller member.

34. In a motion transmitting mechanism the combination with a controlled member and a controller member, of a flrst and second fluid channel extending from one to the other, means to supply fluid pressure to said channels, means associated with the members to establish equal pressures in said channels, said means including a first resistance in each channel connected for inverse variation upon opposite movement of the controller member to efiect a greater pressure in one of the channels, said means also including a second resistance in each channel consociated with the controlled member, and means responsive to said greater pressure to efiect movement of the controlled member, and thereby automatic adjustment of the second resistances to equalize the channel pressures and stop said controlled member movement. 1

35. A remote control mechanism for a shiftable rate determining part of a machine tool transmission, incremental movement of the part efiecting infinitesimal variation of rate, said part being oppositely movable whereby the rate may be increased or decreased, comprising a distant controller for determining movement of the part to any position in either direction in accordance with movement of the controller including a pair of fluid channels extending from the controller to the part, a pair of opposed pistons connected to the respective channels for eifecting actuation of the part, meansto maintain a continuous flow through said channels, means associated with the controller upon movement thereof to create a greater pressure in the channel and on the piston which will effect movementlof the part-in the desired direction, and means associated with thepart automatically effective upon movement thereof through a distance proportional to the 

